EP0716238A1 - Light weight bearing apparatus and assembly method - Google Patents
Light weight bearing apparatus and assembly method Download PDFInfo
- Publication number
- EP0716238A1 EP0716238A1 EP95114915A EP95114915A EP0716238A1 EP 0716238 A1 EP0716238 A1 EP 0716238A1 EP 95114915 A EP95114915 A EP 95114915A EP 95114915 A EP95114915 A EP 95114915A EP 0716238 A1 EP0716238 A1 EP 0716238A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- sleeve
- liner
- insert
- longitudinal axis
- bearing apparatus
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Ceased
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
- F16C33/06—Sliding surface mainly made of metal
- F16C33/08—Attachment of brasses, bushes or linings to the bearing housing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C17/00—Sliding-contact bearings for exclusively rotary movement
- F16C17/12—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load
- F16C17/22—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load with arrangements compensating for thermal expansion
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S384/00—Bearings
- Y10S384/90—Cooling or heating
- Y10S384/912—Metallic
Definitions
- the present invention relates generally to light weight bearings and methods of manufacturing same and, more particularly, to bearings of the type including a light weight outer sleeve or carrier which is interference fit connected with a heavier internal insert, liner or load bearing surface.
- Assembly of bearings of this type includes developing a relative temperature differential between the outer sleeve and the inner liner whereby, after inserting the liner into the sleeve, a radial interference connection is established when the sleeve and inner liner composite connection reaches an equilibrium temperature.
- the basic engineering problem to be solved has been one of providing suitable bearing working surfaces, such as of a leaded bronze material, to absorb the bearing loads from rotating parts while simultaneously employing lighter weight materials, such as aluminum alloys, to transmit the mechanical loads and the frictional heat generated by the working surfaces, to a larger overall housing structure.
- a number of adhesive bonding methods have been attempted whereby a leaded bronze insert is joined to an outer light weight sleeve carrier using an adhesive substance. According to this design the leaded bronze insert provides a bearing working surface while the light weight carrier provides mechanical integrity.
- bearings using the adhesive bonding methods often experience fluid leakage between the bonded pieces. Of course, this fluid leakage is not usually designed into the product and typically degrades bearing performance.
- bonding methods are sensitive to bearing geometry specifications as well as process variations, cleanliness, and bonding material composition. The variations in assembly processes include surface preparation and cleanliness, adhesive application and its uniformity, and curing methodologies. In-service conditions such as loading, pressure, temperature and fluid properties can mechanically damage and/or chemically alter the bond joint causing it to fail which, in turn, degrades the service life of the apparatus and may induce secondary failures.
- the adhesive used to connect the components often tends to act as a thermal insulator, thus inhibiting the ability of the leaded bronze insert to dissipate the heat developed through friction, into the surrounding structure.
- bearing load capacity is impaired due to heat build-up, which directly reduces the viscosity and hydrodynamic load capacity of the working fluid between the moving parts in the bearing.
- adhesives are subject to possible long term degradation in service due to thermal exposure such as extremes in temperature, thermal cycling and differential part expansion.
- the adhesives are susceptible to chemical attack which can lead to catastrophic failure of the bond joint itself.
- process variations make it virtually impossible to accurately predict bond joint life.
- One solution is to calculate an anticipated bond joint life and replace the bearing well in advance of its life expectancy. However, this is usually commercially unfeasible.
- An alternative strategy to the various adhesive bonding methods mentioned above includes the use of elastomeric seals between two or more light weight bearing materials which are mechanically assembled into a composite bearing structure.
- Such bearings are susceptible to leakage due to degradation of the seals such as by chemical attack, thermal cycling, differential expansion of the various bearing parts and wide temperature extremes.
- elastomeric seals tend to wear prematurely due to relative motion between or among the various pieces comprising the composite bearing structure. Weakened bearing seals may extrude through clearance gaps or otherwise rip, tear, or abrade. Further, overall bearing load capability may be impaired due to the effects of manufacturing tolerances of each of the individual parts comprising the composite bearing assembly.
- a third alternative light weight bearing construction strategy includes a metallurgical bonding approach whereby a bronze liner is brazed or soldered to a light weight aluminum carrier. Casting processes have also been attempted with varying degrees of success. Overall, metallurgical bonding overcomes most of the leakage, heat conductance and part size tolerance problems associated with the adhesive bonding and multiple piece elastomeric sealing methods discussed above. However, the differential thermal expansion experienced between the bronze liner and aluminum carrier tends to negatively influence overall durability problems, particularly in bearings of large diameter or high length/diameter (L/D) ratios. Also, material properties such as strength, ductility, and thermal expansion can very within a single bond zone, particularly in cast bearings, due to alloying, different rates of cooling or solidification and for other reasons.
- MMCs Metal matrix composites
- problems have been encountered with reduced material ductility in the MMCs, and material property variability remains a troublesome engineering problem.
- light weight bearings employing the metallurgical bonding techniques also remain highly susceptible to process variations and tend to be quite expensive to produce.
- the subject invention provides a simple mechanical technique to effect a unitary finished bearing part which combines the load carrying and wear properties of a primary bearing material with a lighter carrier material. More particularly, in accordance with the present invention, a leaded bronze liner insert is interference connected by a radial shrink fit to an outer aluminum alloy carrier sleeve housing sleeve structure.
- the characteristics of the mechanical joint between the separate pieces is reliably predictable and does not significantly vary from part to part or over time in service as do the characteristics of the adhesive or metallurgical bonding joints.
- the two-piece assembly of the subject invention behaves as if it were a single piece, eliminating the relative motion between the bearing parts which occurs in typical multiple piece assemblies utilizing elastomeric seals as described above.
- the mechanical joint between the insert and sleeve of the present invention permits the use of a wider range of materials and is significantly less sensitive to process variations than the bonded part bearings discussed above.
- One significant advantage of the present invention over bearings manufactured using an adhesive bonding technique is that a well-defined, high conductivity heat dissipation path is established between the leaded bronze insert and aluminum alloy sleeve through a radial interference fit connection therebetween. This eliminates the insulative effects of the adhesive material itself which effects are compounded by air gaps in the adhesive material.
- Other advantages of the present invention over bearings fabricated using adhesive bonding techniques include a separation of the load carrying function from the leakage prevention function, improved leakage control by a more positive sealing system which includes an O-ring, and elimination of bond and seal degradation due to breakdown of the adhesive over time while in service. Reduced susceptibility to process variations as well as improved manufacturing control are realized by the simple and efficient two piece construction of the present invention.
- Another advantage of the present invention over the mechanical multi-piece bearings discussed above is an improved load and heat dissipation capacity through a well defined load path along the full axial joint length between the leaded bronze liner in intimate contact with the aluminum sleeve or carrier. Both assembly time and the likelihood of misassembly or damage during manufacture are reduced as a result of the simple two piece construction of the present bearing assembly. This construction also reduces tolerance stack-up and misalignment which can result between the parts of a multi-piece bearing and which can lead to problems such as seal extrusion through gaps and unwanted relative motion between parts.
- a further advantage of the present invention relative to bearings fabricated using metallurgical bonding techniques is a reduced sensitivity to thermal expansion and thermal cycling, both of which act to weaken the metallurgically bonded joint.
- thermal expansion effects on joint integrity and durability can be quantitatively assessed and thereby anticipated and controlled.
- bearing apparatus 10 includes an outer carrier or sleeve 12 which surrounds and holds fixed therein an elongated cylindrical liner or insert 14 .
- the insert is provided with an axial bore 16 having a longitudinal axis L for receiving an operatively associated external rotating or reciprocating member (not shown).
- the bearing apparatus 10 is a composite two piece structure and generally includes a thrust flange region A , a threaded region B , a cylindrical section C , and an optional tail section D . Each of the bearing sections will be described in detail below.
- the bearing apparatus 10 is illustrated in axial cross section and elevational face end views respectively.
- the liner insert 14 is substantially cylindrical and is preferably formed of a leaded bronze alloy material such as a 20% lead alloy available from Western Reserve Manufacturing Co. as #520 although other materials may be used, for example, any bronze, brass, or other alloy having suitable bearing characteristics.
- the carrier sleeve 12 is also substantially cylindrical and is preferably formed of an aluminum alloy such as AMS 4145 (4032 forging stock) although other materials may be used, for example, 2024, 6061 or other aluminum alloy, matrix composites or any other material with suitable mechanical properties, including non-metallic materials such as plastics or ceramics.
- the insert is joined to the outer carrier sleeve 12 through a separate pair of independent radial interference fit connections 18 , 20 .
- male threads 22 on the insert 14 intermate with female threads 24 on the carrier sleeve 12 to define a spiral pattern radial interference fit connection 18 .
- an interior smooth bore 26 provided in the sleeve 12 engages a cylindrical outer surface 28 of the liner 14 to form an uninterrupted cylindrical radial interference fit connection 20 .
- the insert 14 is substantially cylindrical within both threaded region B and the cylindrical section C of the bearing apparatus 10 .
- the insert 14 includes an enlarged radially extending integral flange 30 preferably formed of the same material comprising the remainder of the insert 14 which is preferably the above noted leaded bronze.
- the flange 30 includes a planar face surface 32 which is disposed substantially perpendicular to the longitudinal axis L .
- the face surface 32 provides a bearing thrust surface suitable for engagement with a gear or other mechanism which may be fixed to and rotate with an operatively associated external shaft member (not shown) within the bore 16 .
- the face surface 32 defines a substantially annular smooth raceway surface upon which a gear or other rotating thrust compensating member may contact.
- a small relief 34 is machined into the otherwise smooth face surface 32 of the flange 30 for improved lubricating capabilities.
- the relief 34 is circular and continuous along the bore 16 for an even distribution of lubricating fluids.
- the thrust flange 30 further defines a substantially annular smooth connecting surface 36 opposite the face side 32 thereof which is adapted to engage corresponding sealing surfaces 40 , 42 provided on a substantially planar face 44 of the outer sleeve 12 .
- the connecting surface 36 lies in a plane which is substantially perpendicular to the longitudinal axis L and parallel to the plane of the face side 32 .
- the inner sealing surface 40 and outer sealing surface 42 establish intimate contact with the smooth connecting surface 36 of the flange 30 to define a pair of annular mechanical seals 46 and 48 respectively when the liner 14 is threaded tightly into the sleeve 12 as illustrated best in FIGURE 2.
- the outer seal 48 provides a first seal against the flow of pressurized fluid into the region between the liner and sleeve.
- the redundant or inner seal 46 of course provides a second annular mechanical interference seal within the outer first seal 48 .
- At least one relief passageway 50 is included in the insert 14 for the purposes of providing a pressure relief at the interface region 52 between the sleeve 12 and insert 14 .
- the relief passageway 50 defines a fluid escape between the sleeve/insert interface and an annular relief 54 machined into the face surface 44 of the sleeve 12 .
- the outer sleeve 12 includes a continuous circumferential groove 60 provided between the inner sealing surface 40 and the outer sealing surface 42 .
- the groove 60 is adapted to receive an elastomeric sealing member 62 which, in the preferred embodiment is a rubber O-ring.
- each of the inner and outer sealing surfaces 40 , 42 of the liner mechanically engage the connecting surface 36 of the flange member 30 .
- the O-ring 62 is compressed between the liner and sleeve and entrapped within the groove 60 .
- the groove is slightly "D" shaped to correspond as close as possible to the outer extremities of the flange and sleeve interface. It has been found that the O-ring is most efficient when disposed as close as possible to the outer edge of the flange 30 and sleeve 12 in the radial plane.
- male threads 22 on the insert 14 mate with female threads 24 on the carrier sleeve 12 to define a spiral pattern radial interference fit connection 18 .
- the male threads 22 define a large radial diameter 70 about the longitudinal axis L while the female threads 24 on the carrier sleeve 12 define a smaller radial diameter 72 about the longitudinal axis L .
- the spiral pattern radial interference fit connection 18 is established at the small diameter 72 between the flattened tips 74 of the female threads 24 and the roots 76 of the male threads 22 disposed on the insert 14 .
- FIGURE 4 is an enlargement of the cross-sectional dot and dash portion of FIGURE 2.
- the roots 76 of the male threads 22 at the small diameter 72 establish the spiral radial interference fit connection.
- the forward facing flanks 78 of the male threads 22 engage the rearward facing flanks 80 of the female threads 24 when the insert 14 is threaded into the sleeve 12 such that the surfaces 36 and 44 engage as illustrated in FIGURE 2.
- the roots 82 of the female threads 24 do not engage the flat tips 84 of the male threads 22 .
- the preferred thread joint illustrated in FIGURE 4 employs a modified ACME thread layout wherein the male threads 22 on the liner 14 are cut with a standard stub ACME thread form tool and the female threads 24 on the sleeve 12 are cut with a standard full height ACME thread form tool but with a portion of the cutter tip removed therefrom in order to establish a wider valley section in the female thread than would otherwise be possible without removing excessive amounts of the sleeve material.
- Several other thread forms and manufacturing techniques are also possible.
- the interior smooth bore 26 in sleeve 12 engages the cylindrical outer surface 28 of the liner 12 to form an uninterrupted cylindrical radial interference fit connection 20 .
- both the smooth bore 26 and outer surface 28 are held as close as possible to the small diameter 72 at which the spiral pattern radial interference fit connection 18 is established in the threaded region B .
- positive contact between the liner and sleeve is established in each of the threaded region B and cylindrical section C . This is because of the substantially uniform radial interference fit along the small diameter 72 .
- the dual radial interference fit is preferred because it compensates for radial differential thermal expansion between the liner and sleeve and also serves to provide prevailing torque to prevent rotational movement between the liner and sleeve.
- the preferred dual interference fit shown in the FIGURES provides a positive path for heat conduction between the liner insert working surfaces and the outer sleeve and surrounding support structure (not shown).
- the combined contact area of the interference fit connections 18 , 20 greatly exceeds the thread 22 , 24 contact area on the flanks thereof. Thus it is extremely unlikely that any loosening of the joint will occur.
- the combined spiral pattern and uninterrupted cylindrical radial interference fit connections 18 , 20 ensure a positive support of the liner insert 14 along its full length. Support is evenly distributed about the longitudinal axis L , to transmit mechanical forces to the surrounding housing structure without distortion of the liner working surfaces due to inadequate support.
- the tail section D of the light weight bearing apparatus 10 includes a circular relief 90 established along the longitudinal axis L between the back face 92 of the liner insert 14 and a secondary front face 94 of the carrier sleeve 12 .
- Axial clearance is thereby provided along the longitudinal axis L in order to accommodate differential axial thermal expansion between the liner 14 and the sleeve 12 .
- This arrangement is preferred because it permits minimal distortion of the thrust face 32 even in bearings having high length to diameter L/D ratios.
- FIGURES 5 and 6 show alternative embodiments of the bearing apparatus of the present invention.
- like elements will be referred to by like numerals with a primed (') suffix, and new elements will be referred to by new numerals.
- FIGURE 5 a first alternative arrangement of the preferred light weight bearing apparatus illustrated in FIGURES 1-4 is illustrated wherein the groove 60' is provided in the liner insert 14' rather than within the carrier sleeve 12' as earlier described.
- the groove 60' accommodates a corresponding O-ring 62' which is preferably of sufficient cross-section to be compressed between the liner and sleeve when those two parts are mated such as shown in the FIGURE.
- inner and outer sealing surfaces 40' , 42' are defined in the liner insert 14' rather than in the carrier as earlier described.
- the inner and outer sealing surfaces 40', 42' establish inner and outer annular mechanical seals 46' , 48' , respectively, in a manner equivalent to that discussed in conjunction with the first preferred embodiment illustrated in FIGURE 2.
- the bearing assembly of FIGURE 5 is functionally equivalent to that shown in FIGURE 2.
- the bearing apparatus of FIGURE 2 may be preferred over that shown in FIGURE 5 when manufacturability is a major concern. That is, it has been found that it is generally more difficult to machine the groove 60' into the liner insert 14' as illustrated in FIGURE 5 than it is to machine the carrier 12 as shown in FIGURE 2. In situations where the manufacturability is not a major concern, however, it is possible that the bearing apparatus 10' shown in FIGURE 5 may be preferred under certain circumstances or for particular applications.
- FIGURE 6 illustrates a radially oriented seal arrangement as a second alternative embodiment whereby the contacting surface 36'' of the liner insert 14'' engages the face surface 44'' of the carrier 12'' at a single uninterrupted annular mechanical seal 96 .
- An O-ring 62'' is entrapped between the sleeve and insert at an interface region 52'' provided between the seal 96 and the threaded region B'' of the light weight bearing apparatus 10'' illustrated in the FIGURE.
- the bearing apparatus illustrated in FIGURE 6 may be preferred over the first two embodiments discussed above. However, it has been found that the embodiment illustrated in FIGURE 6 subjects the flange to larger bending loads, mainly due to the inboard placement of the O-ring seal and, therefore, may not always be preferred over the arrangements illustrated in FIGURES 1-5.
- the liner 14 and sleeve 12 are machined using well known fabrication techniques such as NC milling, drilling and thread forming procedures well known to those skilled in the art. Also at this machining step, the datum and interface features such as the inner and outer sealing surfaces 40 and 42 are established along with the groove 60 in one of the component parts.
- step 104 the O-ring 62 is inserted into the groove 60 defined in the sleeve 12 at step 102 .
- a thermal differential is established at step 106 between the sleeve and insert to compensate for the interference fit connections 18 and 20 .
- a temperature differential where the sleeve is about 70° hotter than the liner results in a relative radial size differential where the liner is easily threaded into engagement with the sleeve and the faces 36 , 44 fully engage. Larger temperature differential may be necessary to allow longer working time for assembly. Other temperatures would be required for other material compositions.
- step 108 the liner is assembled into the sleeve and torqued to the appropriate specifications.
- the assembly of the liner into the sleeve is of course performed while the parts are maintained at the temperature differential.
- the assembled bearing is stabilized to room temperature at step 110. It is during the stabilization within which the interference fit connections are established. Generally, the relative radial growths between the liner and sleeve cause the liner to become captured within the sleeve at the smaller diameter dimension 72 .
- the completed assembly is cycled to its anticipated lowest and highest operating temperatures at step 112.
- the bearing assembly is maintained above 290° for five minutes and then below -35° for five minutes constituting a complete cycle.
- a plurality of these cycles may be performed in order to relieve any stresses which may have been imparted into the bearing structure during the assembly or stabilization steps 108, 110.
- the bearing is returned to a normal room temperature where finish machining operations are performed at step 114.
- finish machining work does not significantly elevate the temperature of a bearing assembly to impart any additional stress or otherwise damage the part.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Sliding-Contact Bearings (AREA)
- Mounting Of Bearings Or Others (AREA)
Abstract
A two-piece mechanical joint light weight bearing includes a liner (14) of leaded bronze joined with an outer sleeve (12) of an aluminum alloy. The joint consists of a straight cylindrical section (20) and a threaded section (18) along the axial direction of the bearing. Both the threaded (18) and straight (20) cylindrical sections of the bearing employ a radial interference fit to ensure positive contact between the bronze and aluminum materials (12,14). The interference fit is selected to compensate for radial differential thermal expansion between the liner (14) and sleeve (12) and provides a prevailing torque to prevent rotational movement between the liner (14) and sleeve (12). A molded elastomer seal (62) is located on a first end of the bearing to provide a seal between the liner (14) and sleeve (12). A method of assembling the bearing includes establishing a relative temperature differential between the component parts, assembling the component parts while held at the differential temperature and then stabilizing the completed assembly at room temperature.
Description
- The present invention relates generally to light weight bearings and methods of manufacturing same and, more particularly, to bearings of the type including a light weight outer sleeve or carrier which is interference fit connected with a heavier internal insert, liner or load bearing surface. Assembly of bearings of this type includes developing a relative temperature differential between the outer sleeve and the inner liner whereby, after inserting the liner into the sleeve, a radial interference connection is established when the sleeve and inner liner composite connection reaches an equilibrium temperature.
- Prior to the instant invention, several alternative approaches have been explored in the construction of light weight bearings with varying degrees of success. The basic engineering problem to be solved has been one of providing suitable bearing working surfaces, such as of a leaded bronze material, to absorb the bearing loads from rotating parts while simultaneously employing lighter weight materials, such as aluminum alloys, to transmit the mechanical loads and the frictional heat generated by the working surfaces, to a larger overall housing structure.
- A number of adhesive bonding methods have been attempted whereby a leaded bronze insert is joined to an outer light weight sleeve carrier using an adhesive substance. According to this design the leaded bronze insert provides a bearing working surface while the light weight carrier provides mechanical integrity. However, bearings using the adhesive bonding methods often experience fluid leakage between the bonded pieces. Of course, this fluid leakage is not usually designed into the product and typically degrades bearing performance. In addition, bonding methods are sensitive to bearing geometry specifications as well as process variations, cleanliness, and bonding material composition. The variations in assembly processes include surface preparation and cleanliness, adhesive application and its uniformity, and curing methodologies. In-service conditions such as loading, pressure, temperature and fluid properties can mechanically damage and/or chemically alter the bond joint causing it to fail which, in turn, degrades the service life of the apparatus and may induce secondary failures.
- In addition to the acute sensitivity of these bearings to the bonding process variations, the adhesive used to connect the components often tends to act as a thermal insulator, thus inhibiting the ability of the leaded bronze insert to dissipate the heat developed through friction, into the surrounding structure. Overall, bearing load capacity is impaired due to heat build-up, which directly reduces the viscosity and hydrodynamic load capacity of the working fluid between the moving parts in the bearing. Further, adhesives are subject to possible long term degradation in service due to thermal exposure such as extremes in temperature, thermal cycling and differential part expansion. Still further, the adhesives are susceptible to chemical attack which can lead to catastrophic failure of the bond joint itself. Lastly, process variations make it virtually impossible to accurately predict bond joint life. One solution is to calculate an anticipated bond joint life and replace the bearing well in advance of its life expectancy. However, this is usually commercially unfeasible.
- An alternative strategy to the various adhesive bonding methods mentioned above includes the use of elastomeric seals between two or more light weight bearing materials which are mechanically assembled into a composite bearing structure. Such bearings, however, are susceptible to leakage due to degradation of the seals such as by chemical attack, thermal cycling, differential expansion of the various bearing parts and wide temperature extremes. In addition, elastomeric seals tend to wear prematurely due to relative motion between or among the various pieces comprising the composite bearing structure. Weakened bearing seals may extrude through clearance gaps or otherwise rip, tear, or abrade. Further, overall bearing load capability may be impaired due to the effects of manufacturing tolerances of each of the individual parts comprising the composite bearing assembly. This can result in excessive misalignment between the working surfaces of the bearing and the associated rotating or otherwise moving parts. Additionally, discontinuities such as clearance gaps between the parts disrupt the efficient conduction of frictional thermal energy away to the surrounding structure, impairing the overall load carrying ability of the bearing. Lastly, as the number of pieces comprising the composite bearing structure increases, the likelihood of improper assembly increases as does the overall labor, raw material, and resultant manufacturing cost. This becomes significant over the total product service life when multiple assemblies or overhauls occur.
- A third alternative light weight bearing construction strategy includes a metallurgical bonding approach whereby a bronze liner is brazed or soldered to a light weight aluminum carrier. Casting processes have also been attempted with varying degrees of success. Overall, metallurgical bonding overcomes most of the leakage, heat conductance and part size tolerance problems associated with the adhesive bonding and multiple piece elastomeric sealing methods discussed above. However, the differential thermal expansion experienced between the bronze liner and aluminum carrier tends to negatively influence overall durability problems, particularly in bearings of large diameter or high length/diameter (L/D) ratios. Also, material properties such as strength, ductility, and thermal expansion can very within a single bond zone, particularly in cast bearings, due to alloying, different rates of cooling or solidification and for other reasons.
- Properties of the metallurgical bonds also tend to vary over time, due to thermal exposure, diffusion and migration of constituents, and other effects such as work hardening or fatigue. Metal matrix composites (MMCs) have been used in an attempt to reduce or eliminate differential thermal expansion in bearings which rely on metallurgical bonds. However, problems have been encountered with reduced material ductility in the MMCs, and material property variability remains a troublesome engineering problem. In any case, light weight bearings employing the metallurgical bonding techniques also remain highly susceptible to process variations and tend to be quite expensive to produce.
- The subject invention provides a simple mechanical technique to effect a unitary finished bearing part which combines the load carrying and wear properties of a primary bearing material with a lighter carrier material. More particularly, in accordance with the present invention, a leaded bronze liner insert is interference connected by a radial shrink fit to an outer aluminum alloy carrier sleeve housing sleeve structure. The characteristics of the mechanical joint between the separate pieces is reliably predictable and does not significantly vary from part to part or over time in service as do the characteristics of the adhesive or metallurgical bonding joints. The two-piece assembly of the subject invention behaves as if it were a single piece, eliminating the relative motion between the bearing parts which occurs in typical multiple piece assemblies utilizing elastomeric seals as described above. The mechanical joint between the insert and sleeve of the present invention permits the use of a wider range of materials and is significantly less sensitive to process variations than the bonded part bearings discussed above.
- One significant advantage of the present invention over bearings manufactured using an adhesive bonding technique is that a well-defined, high conductivity heat dissipation path is established between the leaded bronze insert and aluminum alloy sleeve through a radial interference fit connection therebetween. This eliminates the insulative effects of the adhesive material itself which effects are compounded by air gaps in the adhesive material. Other advantages of the present invention over bearings fabricated using adhesive bonding techniques include a separation of the load carrying function from the leakage prevention function, improved leakage control by a more positive sealing system which includes an O-ring, and elimination of bond and seal degradation due to breakdown of the adhesive over time while in service. Reduced susceptibility to process variations as well as improved manufacturing control are realized by the simple and efficient two piece construction of the present invention.
- Another advantage of the present invention over the mechanical multi-piece bearings discussed above is an improved load and heat dissipation capacity through a well defined load path along the full axial joint length between the leaded bronze liner in intimate contact with the aluminum sleeve or carrier. Both assembly time and the likelihood of misassembly or damage during manufacture are reduced as a result of the simple two piece construction of the present bearing assembly. This construction also reduces tolerance stack-up and misalignment which can result between the parts of a multi-piece bearing and which can lead to problems such as seal extrusion through gaps and unwanted relative motion between parts.
- A further advantage of the present invention relative to bearings fabricated using metallurgical bonding techniques is a reduced sensitivity to thermal expansion and thermal cycling, both of which act to weaken the metallurgically bonded joint. In the construction of the present invention, thermal expansion effects on joint integrity and durability can be quantitatively assessed and thereby anticipated and controlled.
- Still other advantages and benefits of the invention will become apparent to those skilled in the art upon a reading and understanding of the following detailed description.
- The invention may take physical form in certain parts and arrangements of parts, a preferred embodiment and alternative embodiments which will be described in detail in this specification and illustrated in the accompanying drawings which form a part hereof and wherein:
- FIGURE 1 is a schematic perspective view of the light weight bearing apparatus according to the present invention;
- FIGURE 2 is an axial cross-sectional view of the bearing apparatus illustrated in FIGURE 1 taken through line 2-2;
- FIGURE 3 is an elevated face end view of the bearing apparatus shown in FIGURE 1 taken through line 3-3;
- FIGURE 4 is an enlarged cross-sectional view of the dot-and-dash cross-sectional portion of the bearing apparatus illustrated in FIGURE 2;
- FIGURE 5 is an axial cross-sectional view of the bearing apparatus shown in FIGURE 1 taken along line 2-2 illustrating a first alternative embodiment;
- FIGURE 6 is an axial cross-sectional view of the bearing apparatus shown in FIGURE 1 taken along line 2-2 illustrating a second alternative embodiment; and,
- FIGURE 7 is a flow chart illustrating a preferred method of manufacturing the light weight bearing apparatus of the instant invention.
- Referring now to the drawings wherein the showings are for the purposes of illustrating the preferred and alternative embodiments of the invention only and not for the purposes of limiting same, the FIGURES show a light
weight bearing apparatus 10 and anassembly method 100 for manufacturing same. As illustrated in FIGURE 1, bearingapparatus 10 includes an outer carrier orsleeve 12 which surrounds and holds fixed therein an elongated cylindrical liner orinsert 14. The insert is provided with anaxial bore 16 having a longitudinal axis L for receiving an operatively associated external rotating or reciprocating member (not shown). The bearingapparatus 10 is a composite two piece structure and generally includes a thrust flange region A, a threaded region B, a cylindrical section C, and an optional tail section D. Each of the bearing sections will be described in detail below. - With continued reference to FIGURE 1 but with additional reference to FIGURES 2 and 3, the bearing
apparatus 10 is illustrated in axial cross section and elevational face end views respectively. Theliner insert 14 is substantially cylindrical and is preferably formed of a leaded bronze alloy material such as a 20% lead alloy available from Western Reserve Manufacturing Co. as #520 although other materials may be used, for example, any bronze, brass, or other alloy having suitable bearing characteristics. Thecarrier sleeve 12 is also substantially cylindrical and is preferably formed of an aluminum alloy such as AMS 4145 (4032 forging stock) although other materials may be used, for example, 2024, 6061 or other aluminum alloy, matrix composites or any other material with suitable mechanical properties, including non-metallic materials such as plastics or ceramics. - The insert is joined to the
outer carrier sleeve 12 through a separate pair of independent radial interferencefit connections male threads 22 on theinsert 14 intermate withfemale threads 24 on thecarrier sleeve 12 to define a spiral pattern radial interferencefit connection 18. At the cylindrical section C, an interiorsmooth bore 26 provided in thesleeve 12 engages a cylindricalouter surface 28 of theliner 14 to form an uninterrupted cylindrical radial interferencefit connection 20. - The
insert 14 is substantially cylindrical within both threaded region B and the cylindrical section C of thebearing apparatus 10. However, in the flange region A, theinsert 14 includes an enlarged radially extendingintegral flange 30 preferably formed of the same material comprising the remainder of theinsert 14 which is preferably the above noted leaded bronze. Theflange 30 includes aplanar face surface 32 which is disposed substantially perpendicular to the longitudinal axis L. Theface surface 32 provides a bearing thrust surface suitable for engagement with a gear or other mechanism which may be fixed to and rotate with an operatively associated external shaft member (not shown) within thebore 16. Theface surface 32 defines a substantially annular smooth raceway surface upon which a gear or other rotating thrust compensating member may contact. - A
small relief 34 is machined into the otherwisesmooth face surface 32 of theflange 30 for improved lubricating capabilities. In the preferred embodiment, therelief 34 is circular and continuous along thebore 16 for an even distribution of lubricating fluids. - The
thrust flange 30 further defines a substantially annular smooth connectingsurface 36 opposite theface side 32 thereof which is adapted to engage corresponding sealing surfaces 40, 42 provided on a substantiallyplanar face 44 of theouter sleeve 12. The connectingsurface 36 lies in a plane which is substantially perpendicular to the longitudinal axis L and parallel to the plane of theface side 32. - The
inner sealing surface 40 and outer sealingsurface 42 establish intimate contact with the smooth connectingsurface 36 of theflange 30 to define a pair of annularmechanical seals liner 14 is threaded tightly into thesleeve 12 as illustrated best in FIGURE 2. Theouter seal 48 provides a first seal against the flow of pressurized fluid into the region between the liner and sleeve. The redundant orinner seal 46 of course provides a second annular mechanical interference seal within the outerfirst seal 48. - Further in connection with the flange region A, at least one
relief passageway 50 is included in theinsert 14 for the purposes of providing a pressure relief at theinterface region 52 between thesleeve 12 andinsert 14. Therelief passageway 50 defines a fluid escape between the sleeve/insert interface and anannular relief 54 machined into theface surface 44 of thesleeve 12. - Lastly in connection with the flange region A, the
outer sleeve 12 includes a continuouscircumferential groove 60 provided between theinner sealing surface 40 and theouter sealing surface 42. Thegroove 60 is adapted to receive anelastomeric sealing member 62 which, in the preferred embodiment is a rubber O-ring. As best illustrated in FIGURE 2, each of the inner and outer sealing surfaces 40, 42 of the liner mechanically engage the connectingsurface 36 of theflange member 30. While in the position illustrated, the O-ring 62 is compressed between the liner and sleeve and entrapped within thegroove 60. As best shown in FIGURE 3, the groove is slightly "D" shaped to correspond as close as possible to the outer extremities of the flange and sleeve interface. It has been found that the O-ring is most efficient when disposed as close as possible to the outer edge of theflange 30 andsleeve 12 in the radial plane. - Turning now to the threaded region B of the light
weight bearing apparatus 10,male threads 22 on theinsert 14 mate withfemale threads 24 on thecarrier sleeve 12 to define a spiral pattern radial interferencefit connection 18. As best shown in FIGURE 2, themale threads 22 define a largeradial diameter 70 about the longitudinal axis L while thefemale threads 24 on thecarrier sleeve 12 define a smallerradial diameter 72 about the longitudinal axis L. The spiral pattern radial interferencefit connection 18 is established at thesmall diameter 72 between the flattenedtips 74 of thefemale threads 24 and theroots 76 of themale threads 22 disposed on theinsert 14. The details of the spiral interferencefit connection 18 are best illustrated FIGURE 4 which is an enlargement of the cross-sectional dot and dash portion of FIGURE 2. Theroots 76 of themale threads 22 at thesmall diameter 72 establish the spiral radial interference fit connection. In addition, the forward facing flanks 78 of themale threads 22 engage the rearward facingflanks 80 of thefemale threads 24 when theinsert 14 is threaded into thesleeve 12 such that thesurfaces roots 82 of thefemale threads 24 do not engage theflat tips 84 of themale threads 22. - The preferred thread joint illustrated in FIGURE 4 employs a modified ACME thread layout wherein the
male threads 22 on theliner 14 are cut with a standard stub ACME thread form tool and thefemale threads 24 on thesleeve 12 are cut with a standard full height ACME thread form tool but with a portion of the cutter tip removed therefrom in order to establish a wider valley section in the female thread than would otherwise be possible without removing excessive amounts of the sleeve material. Several other thread forms and manufacturing techniques are also possible. - Referring again to FIGURE 2, at the cylindrical section C, the interior
smooth bore 26 insleeve 12 engages the cylindricalouter surface 28 of theliner 12 to form an uninterrupted cylindrical radial interferencefit connection 20. It is to be noted from FIGURE 2 that both thesmooth bore 26 andouter surface 28 are held as close as possible to thesmall diameter 72 at which the spiral pattern radial interferencefit connection 18 is established in the threaded region B. For both the cylindrical radial interferencefit connection 20 and the spiral radial interferencefit connection 18, positive contact between the liner and sleeve is established in each of the threaded region B and cylindrical section C. This is because of the substantially uniform radial interference fit along thesmall diameter 72. The dual radial interference fit is preferred because it compensates for radial differential thermal expansion between the liner and sleeve and also serves to provide prevailing torque to prevent rotational movement between the liner and sleeve. In addition, the preferred dual interference fit shown in the FIGURES, provides a positive path for heat conduction between the liner insert working surfaces and the outer sleeve and surrounding support structure (not shown). Lastly, the combined contact area of the interferencefit connections thread - Mechanically, the combined spiral pattern and uninterrupted cylindrical radial interference
fit connections liner insert 14 along its full length. Support is evenly distributed about the longitudinal axis L, to transmit mechanical forces to the surrounding housing structure without distortion of the liner working surfaces due to inadequate support. - The tail section D of the light
weight bearing apparatus 10 includes acircular relief 90 established along the longitudinal axis L between theback face 92 of theliner insert 14 and a secondaryfront face 94 of thecarrier sleeve 12. Axial clearance is thereby provided along the longitudinal axis L in order to accommodate differential axial thermal expansion between theliner 14 and thesleeve 12. This arrangement is preferred because it permits minimal distortion of the thrust face 32 even in bearings having high length to diameter L/D ratios. - FIGURES 5 and 6 show alternative embodiments of the bearing apparatus of the present invention. For ease of the illustration and discussion, like elements will be referred to by like numerals with a primed (') suffix, and new elements will be referred to by new numerals. Turning initially to FIGURE 5, a first alternative arrangement of the preferred light weight bearing apparatus illustrated in FIGURES 1-4 is illustrated wherein the groove 60' is provided in the liner insert 14' rather than within the carrier sleeve 12' as earlier described. The groove 60' accommodates a corresponding O-ring 62' which is preferably of sufficient cross-section to be compressed between the liner and sleeve when those two parts are mated such as shown in the FIGURE.
- In addition, the inner and outer sealing surfaces 40', 42' are defined in the liner insert 14' rather than in the carrier as earlier described. The inner and outer sealing surfaces 40', 42' establish inner and outer annular mechanical seals 46', 48', respectively, in a manner equivalent to that discussed in conjunction with the first preferred embodiment illustrated in FIGURE 2.
- Other than the reversed placement of the O-ring and related sealing surfaces shown, the bearing assembly of FIGURE 5 is functionally equivalent to that shown in FIGURE 2. Overall, however, the bearing apparatus of FIGURE 2, may be preferred over that shown in FIGURE 5 when manufacturability is a major concern. That is, it has been found that it is generally more difficult to machine the groove 60' into the liner insert 14' as illustrated in FIGURE 5 than it is to machine the
carrier 12 as shown in FIGURE 2. In situations where the manufacturability is not a major concern, however, it is possible that the bearing apparatus 10' shown in FIGURE 5 may be preferred under certain circumstances or for particular applications. - FIGURE 6 illustrates a radially oriented seal arrangement as a second alternative embodiment whereby the contacting surface 36'' of the liner insert 14'' engages the face surface 44'' of the carrier 12'' at a single uninterrupted annular
mechanical seal 96. An O-ring 62'' is entrapped between the sleeve and insert at an interface region 52'' provided between theseal 96 and the threaded region B'' of the light weight bearing apparatus 10'' illustrated in the FIGURE. In certain applications, the bearing apparatus illustrated in FIGURE 6 may be preferred over the first two embodiments discussed above. However, it has been found that the embodiment illustrated in FIGURE 6 subjects the flange to larger bending loads, mainly due to the inboard placement of the O-ring seal and, therefore, may not always be preferred over the arrangements illustrated in FIGURES 1-5. - With reference lastly to FIGURE 7, the
method 100 of assembling the light weight bearing apparatus shown in FIGURES 1-6 will be discussed. Initially, atstep 102, theliner 14 andsleeve 12 are machined using well known fabrication techniques such as NC milling, drilling and thread forming procedures well known to those skilled in the art. Also at this machining step, the datum and interface features such as the inner and outer sealing surfaces 40 and 42 are established along with thegroove 60 in one of the component parts. - Next, at
step 104, the O-ring 62 is inserted into thegroove 60 defined in thesleeve 12 atstep 102. - A thermal differential is established at
step 106 between the sleeve and insert to compensate for the interferencefit connections faces - Next, at
step 108, the liner is assembled into the sleeve and torqued to the appropriate specifications. The assembly of the liner into the sleeve is of course performed while the parts are maintained at the temperature differential. - The assembled bearing is stabilized to room temperature at
step 110. It is during the stabilization within which the interference fit connections are established. Generally, the relative radial growths between the liner and sleeve cause the liner to become captured within the sleeve at thesmaller diameter dimension 72. - In order to "season" or otherwise stress relieve the bearing
assembly 10, the completed assembly is cycled to its anticipated lowest and highest operating temperatures atstep 112. In the preferred embodiment, the bearing assembly is maintained above 290° for five minutes and then below -35° for five minutes constituting a complete cycle. A plurality of these cycles may be performed in order to relieve any stresses which may have been imparted into the bearing structure during the assembly or stabilization steps 108, 110. - Lastly, the bearing is returned to a normal room temperature where finish machining operations are performed at
step 114. Generally, the finish machining work does not significantly elevate the temperature of a bearing assembly to impart any additional stress or otherwise damage the part. - The invention has been described with reference to the preferred and alternative embodiments. Modification and alterations will occur to others upon reading and understanding of this specification. It is my intention to include all such modifications and alterations insofar as they come within the scope of the appended claims or equivalents thereof.
Claims (20)
- A light weight bearing apparatus comprising:
a sleeve having a first sleeve surface defining an elongate substantially cylindrical aperture along a first longitudinal axis and a second sleeve surface defining a groove in said substantially cylindrical aperture; and,
a substantially cylindrical liner disposed in said sleeve along said first longitudinal axis and having a first liner surface interference fit connected to said first sleeve surface and a second liner surface interference fit connected to said groove. - The light weight bearing apparatus according to claim 1 wherein:
said first and second sleeve surfaces are substantially smooth interior surfaces of the sleeve;
said first and second liner surfaces are substantially smooth exterior surfaces of the liner; and,
at least a one of the first sleeve surface and the first liner surface are adapted to interference fit connect with the other of the first sleeve surface and the first liner surface along a substantially continuous cylindrical interface centered on said first longitudinal axis. - The light weight bearing apparatus according to claim 2 wherein at least a one of the second sleeve surface and the second liner surface are adapted to interference fit connect with the other of the second sleeve surface and the second liner surface along an elongate continuous interface uniformly spaced from said first longitudinal axis.
- The light weight bearing apparatus according to claim 3 wherein:
said second sleeve surface defines a first fastening member along said first longitudinal axis; and,
said second liner surface defines a second fastening member adapted to engage said first fastening member. - The light weight bearing apparatus according to claim 4 wherein said first fastening member comprises a series of internal threads on the sleeve; and,
said second fastening member comprises a series of external threads on the liner, wherein at least a one of the series of internal threads and the series of external threads are adapted to radially interference fit engage the other of the series of internal threads and the series of external threads along a substantially helical interface centered on said first longitudinal axis. - The light weight bearing apparatus according to claim 5 wherein said sleeve defines a substantially annular face surface in a first plane perpendicular to said first longitudinal axis; and,
said liner extends from the sleeve along said first longitudinal axis and includes a lip defining a substantially annular base surface in said first plane adapted to engage said substantially annular face surface. - The light weight bearing apparatus according to claim 6 wherein said substantially annular face surface of the sleeve engages the substantially annular base surface of the liner along an annular continuous interface connection perpendicular to said first longitudinal axis.
- The light weight bearing apparatus according to claim 7 wherein the substantially annular face surface of the sleeve includes means defining a continuous groove in a plane perpendicular to said first longitudinal axis, the groove being adapted to receive a continuous sealing element therein.
- The light weight bearing apparatus according to claim 8 wherein the substantially annular face surface of the sleeve includes at least one relief port having an opening on the annular face surface between the groove and said first longitudinal axis.
- The light weight bearing apparatus according to claim 9 wherein said sleeve is formed of aluminum and said liner is formed of leaded bronze.
- A method of assembling a light weight composite bearing assembly comprising the steps of:
providing a carrier member defining a first elongate interior cylindrical surface disposed along a first longitudinal axis and a second surface defining a groove in said cylindrical surface;
receiving an insert into said carrier member along said first longitudinal axis; and,
interference fit connecting a first elongate exterior cylindrical surface of said insert with said first elongate interior cylindrical surface of said carrier member and a second exterior surface of said insert with said second surface of the carrier member. - The method according to claim 11 further including the step of:
before receiving said insert into said carrier member along said first longitudinal axis, establishing a relative temperature differential between the carrier member and the insert. - The method according to claim 12 wherein the step of establishing said relative temperature differential between the carrier member and the insert includes controlling the temperature of at least a one of the carrier member and insert to provide the carrier member at a temperature greater than a temperature of the insert.
- The method according to claim 13 wherein the step of interference fit connecting the elongate exterior cylindrical surface of said insert with said elongate interior cylindrical surface of said carrier includes the step of establishing an equilibrium relaxed temperature in both said carrier member and said insert.
- The method according to claim 14 wherein the step of establishing said equilibrium relaxed temperature includes the step of cycling the assembly between maximum and minimum operating temperature at least one time to relieve stresses induced during assembly.
- A bearing apparatus comprising:
a carrier member having i) a substantially cylindrical first carrier surface and ii) an elongate helical second carrier surface; and,
an insert within said carrier member having i) a substantially cylindrical first insert surface interference fit connected to said first carrier surface and ii) an elongate helical second insert surface interference fit connected to said second carrier surface. - The bearing apparatus according to claim 16 wherein said carrier member is aluminum and said insert is leaded bronze.
- The bearing apparatus according to claim 17 wherein said carrier member defines a substantially annular face surface in a first plane perpendicular to a longitudinal axis of said cylindrical first carrier surface; and,
said insert extends from said carrier member along said first longitudinal axis and includes a lip defining a substantially annular base surface in said first plane adapted to engage said substantially annular face surface. - The bearing apparatus according to claim 18 wherein said substantially annular face surface of the carrier member engages the substantially annular base surface of the insert along an annular continuous interface connection perpendicular to said longitudinal axis.
- The bearing apparatus according to claim 19 further comprising an elastomeric seal disposed between said substantially annular face surface of the carrier member and the substantially annular base surface of said insert.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US08/351,942 US5544955A (en) | 1994-12-08 | 1994-12-08 | Light weight bearing apparatus and assembly method |
US351942 | 1994-12-08 |
Publications (1)
Publication Number | Publication Date |
---|---|
EP0716238A1 true EP0716238A1 (en) | 1996-06-12 |
Family
ID=23383100
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP95114915A Ceased EP0716238A1 (en) | 1994-12-08 | 1995-09-21 | Light weight bearing apparatus and assembly method |
Country Status (3)
Country | Link |
---|---|
US (1) | US5544955A (en) |
EP (1) | EP0716238A1 (en) |
JP (1) | JPH08226436A (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8162552B2 (en) | 2006-09-25 | 2012-04-24 | Research In Motion Limited | Ramped-key keyboard for a handheld mobile communication device |
US9587729B2 (en) | 2009-11-12 | 2017-03-07 | Schaeffler Technologies AG & Co. KG | Press connection with a sleeve-like component of sheet metal |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10331061B4 (en) * | 2003-07-09 | 2005-05-19 | Technische Universität Dresden | Annular composite workpieces and cold rolling process for their production |
WO2008124464A1 (en) * | 2007-04-04 | 2008-10-16 | Gkn Sinter Metals, Llc. | Multi-piece thin walled powder metal cylinder liners |
US10364545B2 (en) * | 2016-11-11 | 2019-07-30 | Caterpillar Inc. | Bracket assembly for linkage assemblies of machines |
SE541397C2 (en) * | 2017-12-29 | 2019-09-10 | Indexator Rotator Sys Ab | A bushing, a stator comprising such a bushing and a method of fastening such a bushing |
US11268693B2 (en) * | 2018-02-06 | 2022-03-08 | Illinois Tool Works Inc. | Nozzle assemblies having multiple attachment methods |
FR3094049B1 (en) * | 2019-03-18 | 2021-04-23 | Skf Aerospace France | Spherical ball joint |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2315633A1 (en) * | 1975-06-24 | 1977-01-21 | Taylor Gordon | SHAFT CUSHION |
EP0062712A1 (en) * | 1981-04-09 | 1982-10-20 | Deere & Company | Improved shaft bearing bush and bearing assembly |
GB2187803A (en) * | 1986-03-13 | 1987-09-16 | Daido Metal Co | Bearing units |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4432659A (en) * | 1982-03-12 | 1984-02-21 | Walbro Corporation | Fuel pump armature shaft bearing |
US4509290A (en) * | 1983-03-18 | 1985-04-09 | Stanfield Jr Alvin M | Shutter construction |
US5219231A (en) * | 1987-10-02 | 1993-06-15 | Plastic Bearing Housing Australiasia Pty Ltd. | Split race bearing assemblies |
DE4215715C2 (en) * | 1992-05-13 | 1995-02-16 | Telair Int Cargo Sys Gmbh | Bearing bush |
-
1994
- 1994-12-08 US US08/351,942 patent/US5544955A/en not_active Expired - Fee Related
-
1995
- 1995-09-21 EP EP95114915A patent/EP0716238A1/en not_active Ceased
- 1995-12-08 JP JP7320762A patent/JPH08226436A/en active Pending
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2315633A1 (en) * | 1975-06-24 | 1977-01-21 | Taylor Gordon | SHAFT CUSHION |
EP0062712A1 (en) * | 1981-04-09 | 1982-10-20 | Deere & Company | Improved shaft bearing bush and bearing assembly |
GB2187803A (en) * | 1986-03-13 | 1987-09-16 | Daido Metal Co | Bearing units |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8162552B2 (en) | 2006-09-25 | 2012-04-24 | Research In Motion Limited | Ramped-key keyboard for a handheld mobile communication device |
US8449208B2 (en) | 2006-09-25 | 2013-05-28 | Research In Motion Limited | Ramped-key keyboard for a handheld mobile communication device |
US9587729B2 (en) | 2009-11-12 | 2017-03-07 | Schaeffler Technologies AG & Co. KG | Press connection with a sleeve-like component of sheet metal |
DE102009052759B4 (en) * | 2009-11-12 | 2017-03-09 | Schaeffler Technologies AG & Co. KG | Press dressing with a sleeve-like component made of sheet metal |
Also Published As
Publication number | Publication date |
---|---|
JPH08226436A (en) | 1996-09-03 |
US5544955A (en) | 1996-08-13 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP0008766B1 (en) | Threaded connections | |
CA2582653C (en) | Method and apparatus for coupling components | |
US20090000882A1 (en) | Shrink Fitted Caliper Guidance Pins | |
US20080187259A1 (en) | Sliding bearing | |
US5544955A (en) | Light weight bearing apparatus and assembly method | |
US20020094143A1 (en) | Flange bearing | |
EP0287296A2 (en) | Ceramic bearing construction | |
US20030210842A1 (en) | Bearing apparatus for a driving wheel of vehicle | |
US5697651A (en) | Flexible duct joint having a low leakage, pressure-balanced bellows seal | |
US4631973A (en) | Axial retention of gear on shaft | |
US4073550A (en) | Sleeve bearing | |
EP1484495B1 (en) | Externally gimballed joint of a jet pipe | |
US5544896A (en) | Composite face seal | |
US6464228B1 (en) | Method of using a retrofittable severe duty seal for a shaft | |
EP0176614A1 (en) | Offset wall bearing | |
DE112013003392T5 (en) | Compressor wheel with balance correction and positive guidance | |
CA1083211A (en) | Sleeve bearing | |
US20040025626A1 (en) | Connecting rod with ellipitical opening and method for production | |
GB2343226A (en) | Locking plate for semi-cylindrical bearing halves | |
EP0045166B1 (en) | A sleeve bearing half-shell, a journalled bearing assembly comprising such half-shell and a method of forming the assembly | |
US6338491B1 (en) | Rotary shaft seal | |
EP1608880B1 (en) | A spherical bearing arrangement | |
EP0997652A1 (en) | Bearings | |
US6892533B2 (en) | Automatic transmission | |
US20240024961A1 (en) | Hydraulic chuck and expansion sleeves |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): DE FR GB |
|
17P | Request for examination filed |
Effective date: 19960517 |
|
17Q | First examination report despatched |
Effective date: 19971013 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE APPLICATION HAS BEEN REFUSED |
|
18R | Application refused |
Effective date: 19980319 |